US5584777A - Differential cage for absorbing shock mounted in a differential casing - Google Patents

Differential cage for absorbing shock mounted in a differential casing Download PDF

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Publication number
US5584777A
US5584777A US08/444,101 US44410195A US5584777A US 5584777 A US5584777 A US 5584777A US 44410195 A US44410195 A US 44410195A US 5584777 A US5584777 A US 5584777A
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US
United States
Prior art keywords
differential
cage
axle
gears
axle drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/444,101
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English (en)
Inventor
Edmund Sander
Peter Meffert
Peter Hoebel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE4417373A external-priority patent/DE4417373A1/de
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Assigned to DR. ING. H.C.F. PORSCHE AG reassignment DR. ING. H.C.F. PORSCHE AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HOEBEL, PETER, MEFFERT, PETER, SANDER, EDMUND
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Publication of US5584777A publication Critical patent/US5584777A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/082—Differential gearings with gears having orbital motion comprising bevel gears characterised by the arrangement of output shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H2048/387—Shields or washers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2186—Gear casings

Definitions

  • This invention relates to a differential for a motor vehicle, and more particularly, to a differential for the axle drive of a motor vehicle, including a differential case carrying a driving wheel.
  • An axle bolt is disposed in the differential case which carries differential gears.
  • These differential gears mesh with axle shaft gears arranged on axle drive shafts.
  • These axle shaft gears are constructed as bevel gears, and are disposed in a cage, absorbing forces acting in the direction of the axle drive shafts.
  • German Patent document P 43 13 322.3 illustrates and describes a differential for the axle drive of a motor vehicle in the case of which the axle shaft gears are disposed in a cage.
  • This cage absorbs the forces acting in the direction of the axle drive shafts. This frees the differential case from these forces.
  • the differential case can, therefore, have smaller dimensions.
  • This separate cage permits the insertion of the axle shaft gears and the axle bolt before the whole differential is mounted.
  • a differential for the axle drive of a motor vehicle including a differential case carrying a driving wheel.
  • An axle bolt is disposed in the differential case which carries differential gears.
  • These differential gears mesh with axle shaft gears arranged on axle drive shafts.
  • These axle shaft gears are constructed as bevel gears, and are disposed in a cage, absorbing forces acting in the direction of the axle drive shafts.
  • the cage is made of a tube section whose wall has at least two diametrical bores through which the axle drive shafts are lead.
  • the cage consists of a tube section whose wall has at least two diametrical bores for the lead through of the axle drive shafts, particularly during series production, this tube section can be manufactured by dividing a prefabricated or commercially available tube, without any high losses of material. Because of the favorable course of the tension, the wall thickness of such a tube section may be kept relatively narrow so that the corresponding cage is relatively light. In an additional or parallel operating step, at least two diametrical bores through which the axle drive shafts are led are provided in this tube section. A joining or connecting of the cage, as in the case of the cage according to the German Patent document P 43 13 322.3, is not required so that, on the one hand, an additional manufacturing step is saved and, on the other hand, a connecting point having an altered stability is avoided.
  • the differential or its cage can be improved if the cage consists of a cylindrical tube section which is changed to a spherical shape through a deformation operation.
  • This deformation operation is preferably carried out in a non-cutting manner via expanding or rolling round.
  • This deforming operation improves the course of tension in the cage. This is because tension peaks are avoided by eliminating small curvature and corner radii.
  • the bearing of the axle shaft gears is improved, since these gears can be supported in the shape of a spherical segment on the cage.
  • the wall thickness of the cage can again be reduced so that its weight can be further reduced.
  • the weight of the case can be again reduced if two additional diametrical bores are provided which extend approximately at a right angle to those of the axle drive shaft and by which the axle bolt is guided.
  • this differential or the cage can be improved in an advantageous further embodiment by providing the cage with a rectangular cross-section having rounded corners and a stress-specifically adapted wall thickness.
  • this cage can be optimized with respect to its weight as well as its stability.
  • the stress-specifically adapted wall thickness and the rounding of the corners result in optimal stabilities and an optimal course of tension while avoiding tension peaks.
  • This type of a rectangular profile or square tube profile can be produced in a simple and advantageous manner from an extruded profile.
  • a cage of this type having a rectangular or square cross-section may be further improved by curving the walls with the bores for guiding the axle drive shafts toward the inside in the installed condition.
  • an improved defined supporting behavior and a spring effect are obtained for minimizing the load peaks.
  • a lubricating gap construction is achieved through which lubricant can reach the bevel gear guide area.
  • the mounting and the assembly of the differential are facilitated when the axle bolt is surrounded by a guide ring which is arranged between the differential bevel gear and a stop surface.
  • the guide ring has guide extensions which are supported on the cage and guide the cage and the axle bolt relative to one another.
  • the assembly of the differential is further facilitated if one centering sleeve, respectively, is supported on the case.
  • the centering sleeve projects through the cage and centers it and the differential bevel gear in the correct position. On the one hand, this prevents the cage from turning and, on the other hand, an intermediate constructional unit can be created which, after the installation into the case, is arranged in the correct position and is torsionally secured and therefore facilitates the installation of the axle shafts.
  • the gear's running behavior can be improved by a friction reduction.
  • an improved plane support of the axle shaft gears is obtained on the cage.
  • FIG. 1 is a sectional view of a differential according to the invention
  • FIG. 2 is a partially shown sectional view of a modified form of the differential according to the invention.
  • FIGS. 3a-d are views of a first embodiment of a cage
  • FIGS. 4a-d are views of a second embodiment of the cage.
  • FIGS. 5a-d are views of a third variant of the cage.
  • a differential for the axle drive of a motor vehicle includes a driving wheel 1 which is fixedly connected with a differential case 2.
  • the differential case 2 consists of two parts 3 and 4, having a pot-like shape, which have a rotationally symmetrical construction with respect to an axis A--A and may be identical.
  • the free end sections of two mutually opposite axle drive shafts 5, 6, having their longitudinal axes situated on the axis of rotation A--A, project into the differential case 2.
  • an axle shaft gear 7, 8 is, in each case, disposed in a non-rotatable but axially slidable manner.
  • axle shaft gears 7, 8 are constructed as bevel gears and mesh with two opposite differential gears 9, 10 which are also constructed as bevel gears.
  • These differential gears 9, 10 are disposed on an axle bolt 11 having a longitudinal axis B--B extending approximately perpendicular with respect to the axis of rotation A--A.
  • the axle bolt 11 On its top side, the axle bolt 11 has a flange 12 with a larger diameter.
  • the flange 12 is surrounded by a guide element 13 which is guided with some play in a recess 14 formed between the two parts 3 and 4 and the driving wheel 1.
  • a supporting ring 15 rests against the flange 12 of the axle bolt 11.
  • the differential gear 9 is supported on this supporting ring 15.
  • the opposite differential gear 10 rests against a second supporting ring 16 which is welded to the free end of the axle bolt 11.
  • this supporting ring 16 is surrounded by a guide element 18 which is guided with some play in a recess 19 between the two parts 3, 4 of the differential case 2 and the driving wheel 1.
  • the recesses 14, 19 and the guide element 13, 18 are, in each case, designed such that the axle bolt 11 can be slid slightly in the direction of the axis of rotation A--A and the longitudinal axis B--B.
  • axle shaft gears 7, 8 and parts of the differential gears 9,10 are surrounded by a cage 20, as illustrated, for example, in FIGS. 3a to 3d. Because of the forces in the direction of the axis of rotation A--A occurring during the operation of the differential, the axle shaft gears 7, 8 are supported on the case 20. For better contact and for reducing friction, one sliding cup 21, 22 is, respectively, fastened on the cage 20 arranged between the axle shaft gears 7, 8 and the cage 20.
  • the cage 20 shown in detail in FIGS. 3a to 3d includes a tube-like section whose longitudinal axis, in this embodiment, is situated on an axis C--C which is perpendicular to the axis of rotation A--A and the longitudinal axis B--B of the axle bolt.
  • the cage 20 is penetrated by four bores 23 to 26, of which bores 23, 24 and 25, 26 are in each case situated opposite one another in pairs. In this case, the two bores 23, 24 are situated on the axis of rotation A--A.
  • the free ends of the axle drive shafts 5, 6 pass through the bores 23, 24.
  • the bores 25, 26, which are arranged at a right angle thereto, are each situated on the longitudinal axis B--B and are used for accommodating or inserting of the axle bolt 11.
  • a guide ring 27 is arranged between the differential gears (only differential gear 9 is shown here), and the assigned supporting rings 15, 16.
  • the ring surface of the guide ring 27 is used as the running surface between the differential gear 9 and the supporting ring 15.
  • This guide ring 27 extends around the axle bolt 11 and rests against it.
  • Several bent spring arms 28 project from its outer circumference and, on the one side, rest against the wall of the bore 25, 26 of the cage 20 and, on the other side, rest against the supporting ring 15, 16.
  • This guide ring 27 may be made, for example, of plastic and, on the one hand, is used as a running surface between the differential gear and the supporting ring and, on the other hand, as the guiding or centering element by which the axle bolt 11 and the cage 20, during the mounting, are brought into and held in the correct positional alignment.
  • a centering sleeve 29 projects through the bores 23, 24 and in each case extends around the axle drive shaft 5, 6 and, in the area of the shaft leadthrough, rests against the differential case 2.
  • This centering sleeve 29 projects into the interior of the cage 20 and reaches, by means of detents 30, behind a cylindrical extension 31 of the sliding cup 21, 22.
  • an assembly unit comprising the cage, the differential gears and the axle shaft gears, together with the axle bolts, can be centered in the correct position in the differential case 2, before the axle drive shafts 5, 6 are mounted.
  • the axle drive shafts 5, 6 can then, without any further adjusting or positioning operations, be slid into the differential case 2, the corresponding bore in the cage 20 and the respective differential gear.
  • a securing ring 32 which is arranged in a groove 33 of the axle drive shaft 5, 6, the respective axle drive shaft is secured with respect to an unintentional loosening.
  • axle drive shafts 5, 6 are each surrounded with a narrow amount of play by one bearing bush 34, respectively. These are each arranged in the differential case 2 and have sealing lips 35 which rest against the axle drive shaft 5, 6. This provides an interior space in the differential case 2 which is sealed off with respect to the environment.
  • the cage may be modified, as illustrated in FIGS. 4a to 4b.
  • the cage 20a illustrated in FIGS. 4a to 4d also consists of a cylindrical tube section whose shell surface is spherically expanded or rolled round.
  • the longitudinal axis of the cage 20a corresponds to the longitudinal axis B--B.
  • Two diametrical bores 23a, 24a are provided in the shell surface of the cage 20a.
  • the bores 23a, 24a are each disposed on the axis of rotation A--A and are used for receiving or leading through the axle drive shafts 5, 6.
  • the installation of the cage into the differential case 2 takes place such that, with respect to the cage illustrated above, this cage 20a is installed in a manner that is rotated by 90° so that the axle bolt 11 projects through the tube openings 36, 37.
  • the shell surface is penetrated only by two diametrical bores and is therefore weakened less. It is therefore possible to receive a higher load while maintaining the outside dimensions and wall thickness the same.
  • the guide ring 27 is modified such that at least some of the guiding arms 28 are constructed to be longer and are bent such that they rest on or in the tube opening 36, 37 and, therefore, guide and center the cage 20 in the correct position.
  • the cage 20b illustrated in FIGS. 5a to 5d differs mainly by the changed tube profile or the changed tube cross-section.
  • the cage 20b consists of a tube section having an almost square cross-section.
  • a tube section of this type, or a profile tube of this type may be constructed and manufactured, for example, as an extruded profile.
  • the corners of the tube profile are rounded.
  • the edges or corners may be broken or bevelled.
  • the wall thicknesses of the tube are not uniform but, in an adaptation to the load occurring during the operation, are constructed to be continuously decreasing or increasing.
  • cage 20b is penetrated by two diametrical bores 23b, 24b. These two bores are used for the receiving or leading through of the axle drive shafts 5, 6.
  • the lead-through and the receiving of the axle bolt 11 takes place as in the case of cage 20a through the tube openings 36, 37.
  • the arrangement of cage 20b in the differential case 2 takes place analogously to the above-described embodiment.
  • the two opposite walls 38, 39 with the bores 23b and 24b are curved to the inside. By curving the wall to the inside, a certain springing effect is created during the operation, the supporting or running behavior of the axle drive gears is improved and, at the same time, a surrounding lubricating wedge is formed while the supporting forces to be absorbed by the cage are low.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Motor Power Transmission Devices (AREA)
US08/444,101 1994-05-18 1995-05-18 Differential cage for absorbing shock mounted in a differential casing Expired - Fee Related US5584777A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4417373.3 1994-05-18
DE4417373A DE4417373A1 (de) 1993-04-23 1994-05-18 Differential für den Achsantrieb eines Kraftfahrzeuges

Publications (1)

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US5584777A true US5584777A (en) 1996-12-17

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US (1) US5584777A (fr)
EP (1) EP0683333B1 (fr)
JP (1) JPH0840096A (fr)

Cited By (39)

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US5718653A (en) * 1993-08-02 1998-02-17 Borg-Warner Automotive, Inc. Differential assembly for transfer cases and vehicle drivelines
US5857936A (en) * 1996-08-01 1999-01-12 Tochigi Fuji Sangyo Kabushiki Kaisha Differential limiting mechanism of differential apparatus
US5863271A (en) * 1996-08-16 1999-01-26 Hydro-Gear Limited Partnership Controlled traction cartridge and differential
US5897452A (en) * 1996-08-16 1999-04-27 Hydro-Gear Limited Partnership Integrated hydrostatic transaxle with controlled traction differential
US5938558A (en) * 1997-09-19 1999-08-17 Eaton Corporation Limited slip differential and improved differential housing assembly therefor
US5951431A (en) * 1997-05-06 1999-09-14 American Axle & Manufacturing, Inc. Differential unit with optimized assembly window geometry
US5984823A (en) * 1998-08-27 1999-11-16 American Axle & Manufacturing, Inc. Differential with shaft locking mechanism
US6322474B1 (en) 1996-08-23 2001-11-27 Hydro-Gear Limited Partnership Differential for use in a vehicle
US6368242B1 (en) 2000-07-28 2002-04-09 Spicer Technology, Inc. Axle shaft retainer system
EP1219865A1 (fr) * 2000-12-29 2002-07-03 Johann Hay GmbH & Co. KG, Automobiltechnik Assemblage de différentiel et procédé correspondant
WO2003029693A1 (fr) * 2001-10-04 2003-04-10 Peugeot Citroen Automobiles S.A. Differentiel de transmission de couple pour vehicules automobiles
US6575868B1 (en) 2000-04-14 2003-06-10 Hydro-Gear Limited Partnership Transaxle with differential lock mechanism
US6656079B2 (en) * 2000-03-17 2003-12-02 Daimlerchrysler Ag Differential gear and method of making same
US6699154B2 (en) * 2002-01-31 2004-03-02 Visteon Global Technologies, Inc. Differential gear assembly
US6780137B1 (en) 2002-07-26 2004-08-24 Hydro-Gear Limited Partnership Differential lock mechanism
US6840883B2 (en) * 2001-12-20 2005-01-11 Visteon Global Technologies, Inc. Method and design of an automotive differential
FR2864189A1 (fr) * 2003-12-23 2005-06-24 Renault Sas Differentiel avec element de friction decouvrant partiellement la pignonerie
US6981929B2 (en) * 1998-10-22 2006-01-03 Ab Volvo Vehicle differential
US20060243092A1 (en) * 2005-04-29 2006-11-02 Prichard Jonathan P Differential assembly with semi-elliptical assembly window
EP1803972A1 (fr) * 2005-12-27 2007-07-04 ELASIS - Società Consortile per Azioni Assemblage de différentiel, notamment pour un véhicule
US20080051244A1 (en) * 2006-08-28 2008-02-28 Jtekt Corporation Differential gear for vehicle and assembling method of the same
US7454907B1 (en) 1998-11-20 2008-11-25 Hydro-Gear Limited Partnership Hydrostatic transmission
US20090215573A1 (en) * 2008-02-27 2009-08-27 Musashi Seimitsu Industry Co., Ltd. Differential gear
US20090227414A1 (en) * 2005-12-27 2009-09-10 Elasis - Societa Consortile Per Azioni Differential assembly provided with an adjustment device, in particular for motor vehicles
US20090266198A1 (en) * 2008-04-29 2009-10-29 Transform Automotive Llc Laser welded differential casings for vehicle axles
CN101228371B (zh) * 2005-05-24 2011-03-30 Gkn动力传动国际有限公司 具有位于组装开口内的支承板的差速装置
US20110143879A1 (en) * 2007-04-05 2011-06-16 Neumayer Tekfor Holding Gmbh Axle Assembly with a Differential Provided with a Drive Wheel
US20110183803A1 (en) * 2010-01-27 2011-07-28 GM Global Technology Operations LLC Transmission arrangement for a motor vehicle
US20120115669A1 (en) * 2010-11-08 2012-05-10 GKN Driveline Japan Ltd. Differential apparatus
US20120244986A1 (en) * 2009-12-22 2012-09-27 Yuuki Masui Differential apparatus
US20130047779A1 (en) * 2011-08-26 2013-02-28 Robert J. Martin, III Carrier with center backbone and dual lateral cases
US20150024897A1 (en) * 2012-02-24 2015-01-22 SUBA CONULTING, iNC. Torque transmitting assembly
US9207102B2 (en) 2012-06-21 2015-12-08 Dana Automotive Systems Group, Llc Anti-lock brake rotor tone ring cartridge and shaft guide
CN108397535A (zh) * 2017-02-04 2018-08-14 上海汽车集团股份有限公司 反向传动装置以及差速器
US10107374B2 (en) 2015-08-12 2018-10-23 Caterpillar Inc. Differential assembly for a machine
US20190072170A1 (en) * 2016-03-15 2019-03-07 David E. Gall Automotive differential and method of assembling same
US11125317B2 (en) 2019-05-07 2021-09-21 Dana Heavy Vehicle Systems Group, Llc Guide member and a drive unit assembly using the same
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EP0864779B1 (fr) * 1997-03-12 2001-10-17 Volkswagen Aktiengesellschaft Différentiel,en particulier pour l'entraínement d'un essieu d'un véhicule à moteur
DE19727557B4 (de) * 1997-06-28 2005-07-21 Volkswagen Ag Differentialgetriebe mit federbelasteten Abtriebswellen
DE19943920A1 (de) * 1999-09-14 2001-03-15 Man Nutzfahrzeuge Ag Kegelradausgleichsgetriebe für Nutzfahrzeuge
ATE462903T1 (de) * 2006-10-05 2010-04-15 Skf Ab Verfahren zur herstellung eines differentials und differential
DE102007048531A1 (de) * 2007-10-10 2009-04-16 Zf Friedrichshafen Ag Abtriebsflanschanordnung
US8231493B2 (en) 2009-07-27 2012-07-31 Eaton Corporation Differential having improved torque capacity and torque density
US20110021305A1 (en) * 2009-07-27 2011-01-27 Radzevich Stephen P Differential having self-adjusting gearing
US8146458B2 (en) 2009-07-27 2012-04-03 Eaton Corporation Locking differential having improved torque capacity
DE102010054655B4 (de) 2010-09-15 2012-08-09 Sona Blw Präzisionsschmiede Gmbh Differential für Kraftfahrzeuge
DE102011007698A1 (de) * 2011-04-19 2012-10-25 Neapco Europe Gmbh Differenzial mit integrierter Lagerung der Kronenräder
WO2014035869A2 (fr) 2012-08-29 2014-03-06 Eaton Corporation Différentiel bloquant ayant des ressorts de pré-charge en combinaison pour un contact maintenu
WO2014035868A2 (fr) 2012-08-29 2014-03-06 Eaton Corporation Différentiel bloquant ayant un ressort de communication d'amortissement
CN203822999U (zh) 2012-11-19 2014-09-10 伊顿公司 收缩式差速器机构、可收缩的离合差速器及车辆的传动系
US9334941B2 (en) 2013-03-14 2016-05-10 Eaton Corporation Inboard spring arrangement for a clutch actuated differential
JP7217005B2 (ja) * 2019-02-25 2023-02-02 株式会社キャロッセ 二重構造ｌｓｄユニット

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US2364411A (en) * 1943-01-21 1944-12-05 Deere & Co Differential gear
US3057226A (en) * 1958-10-03 1962-10-09 Svenska Aeroplan Ab Planetary differential mechanism
DE1810520A1 (de) * 1968-11-23 1970-06-11 Porsche Kg Ausgleichgetriebe fuer Fahrzeuge,insbesondere Kraftfahrzeuge
US3651713A (en) * 1970-05-01 1972-03-28 Otto Mueller Locks for securing axles to a differential
US4037492A (en) * 1974-11-14 1977-07-26 Volkswagenwerk Aktiengesellschaft Bearing arrangement for axle or shafts provided with rotating gears in a differential gear box
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FR2864189A1 (fr) * 2003-12-23 2005-06-24 Renault Sas Differentiel avec element de friction decouvrant partiellement la pignonerie
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Also Published As

Publication number Publication date
JPH0840096A (ja) 1996-02-13
EP0683333A1 (fr) 1995-11-22
EP0683333B1 (fr) 1997-10-01

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